Metalworking machine



Sept. 22,l 1936. G; c. GRIDLEY ET Ar.

METALWORK ING MACHINE Filed Sept. 2l, 1929 l?. Sheets-Sheet l ATTORNEYS Y l2 Sheets-Sheet 2 Sept, 22 1936. G. o. GRIDLEY ET A1.

METALWORKING MACHINE Filed Sept. 21, 1929 Sept. 22, 1936- G. o. GRIDLEY ET AL f 2,055,434

f METALWORKING MACHINE Filed Sept. 2l, 1929 12'Sheets-Sheet 5` ATTORNEYS Sept. 22, 1936. G. o. GRlDLEY ET AL 2,055,434

METALWORKING MACHINE Filed Sept. 2l, 1929 12 Shee'cs-SheerI 4 6em/"ge Qz'aic? Donald .Malaya/72 rg Z'd/"Z /V/zeeler INVENTORS ATTORNEYS Sept- 22, 1936- v G. o. GRIDLEY ET AL I 2,055,434

V METALWORKING MACHINE Fued sept. 21, 1929 12 sheets-sheet 5 y 6601" erz'd/ey a/zdl /Y/lalzfyamerg fari W/zeeler INVENTORS ATTORNEYS Sept. 22, 1936- G; O. GRIDLEY ET AL METALWORKING MACHINE l2 Sheets-Shes?. 6

Filed sept. 21, 1929 mmm ATTORNEYS Sept. 22, 1936.

METALWORKING MACHINE Filed Sept. 21,1323 l2 Sheets-Sheet '7 12 145m Zl 2@ 222 eorye Q 671476.? ozaZdHMO/l merg fr! W/ er INVENTORS ATTORNEYS G. o. GRIDLEY ET AL ,2,055,434

Sept. 22, 1936. A G. o. GRIDLEY ET 1. 2,055,434

METALWORK ING MACHINE Filed sept. 21, 1923- 12 sheets-shaml 9 ATTORNEYS Sept. 22, l936- ca. o. GRIDLEY ET A1.

METALWORKING MACHINE l2 Sheets-Shea?. l0

Filed sept. 21, 1929 mm wm, Nm wm www Sept- 22, 1936- G. o. GRIDLEY ET AL 2,055,434

METALWORK I NG MACHINE Filed Sept. 2l, A1923 l2 SheetSf-Sheei. 1l

ona/ /Y/l/a/z Wawy 2.33 .244 K 242 [r1/Z lV/fee er INVENTQRS Z4?. '239 il 243 ATTORNEYS i 'i i@ l Sept.` 22, 1936.

G. o. GRIDLEY ET A; 2,055,434 METALWORKING MACHINE Filed Sept. 2l, 1923 12 Sheets-.'Sheerl 12 r/Wg-y/er y INVENTORS ATTORNEYS Patente epi. 22, 'm3

George 0. Gridley and Donald H. Montgomery, Berlin, and Earl Wheeler, Hartford, Conn., as-

signors, by mesne ass ignments, to The New Britain Machine Company, New Britain, Conn., a corporation of Connecticut AApplication september 2i, 1929, serial No. 394,232

96 claims. (ci. .e9-ss) Our invention relates to a metal working machine and will be herein described as embodied ina multiple spindle chucking machine of the station type. It is, however, to be understood that various features of the invention are of broader application and may be embodied in machines of Vother types.

Generally speaking, it is our object Oto provide a machine of sturdy construction for rapidly turning out Work of great accuracy, and a machine of relatively few and simple parts.

It is a more specific object of our invention to provide improved power or driving mechanism which may be a unitarily assembled device.

It is another object to provide-an improved turret or carrier and mounting permitting easy operation combined with rigid supporting.

It is another object to provide an improved simple spindle drive permitting one spindle to v automatically stop upon each indexing of a spindle carrier. h

Another object is to provide improved tool carrier mechanism rigidly mounted and maintained in proper alignment with the Work.

It is still another object to provide improved simple feed mechanism and controls.

A still further object is to provide a simpliiied fluid pressure chucking mechanism assuring proper chucking pressure atY all times. L

Other objects and various features of invention will be hereinafter indicated or will become apparent upon a reading of the specification taken in connection with the illustrative drawings.

In the drawings which show, for illustrative purposes only, one preferred embodiment of the invention- Fig. 1 is a side elevation of a multiple spindle chucking machine illustrating features of the invention;

Fig. 2 is a right hand end elevation of the machine of Fig. 1;

Fig. 3 is a left hand end elevation of the machine of Fig. 1;

Fig.`4 is a vertical substantially central longitudinal sectional view on an enlarged scale of the left half of Fig. 1;

Fig. 5 is a view similar to Fig. 4 illustrating the right hand end of the machine and is substantially a continua "ion of Fig. 4;

, 6 is a sectional view taken substantially in the plane of the line 6-6 of Fig. 4;

Fig. 7 is a sectional view taken substantially in the plane of the line i--l of Fig. 1;

Fig. 8 is a sectional view taken substially in the plane ofthe lineiiof Fig. '7, the turret or spindle carrier being omitted;

Fig. 9 is an enlarged fragmentary view of the right hand turret lock of Fig. 7; l

Fig. 10 is a view similar to Fig. 9 but illustrat- 5 ingthe left end turret lock of Fig. 7

Fig. 11 is a view in side elevation of the left hand end of the machine shown in Fig. 1 with cover members removed and the power unit casing in section;

Fig. 12 is a sectional view taken substantially in the plane of the line I2-i2 of Fig. 13 illustrating a part of the power unit;

Fig. 13 is a sectional view taken substantially ,in the plane of the line i3--i3 ofFig. 11; l5

Fig. 14 is an enlarged sectional view taken substantially in the plane of the line ifi-it of Fig.

Fig. 15 is a sectional view taken substantially in the plane of the line IIE-I5 of- Fig. 4;

Fig. 16 is an enlarged detail of uid pressure chain tightening mechanism;

Fig. 17 is a sectionalview taken substantially in the plane of the line i'l-Il of Fig. 15;

Fig. 18 is a fragmentary sectional view taken substantially in the plane of the line IS--l of Fig. 17 looking in the direction 'of the arrows;

Fig. 19 is asimilar view taken substantially in the plane of the line IQ-IS of Fig. 17 looking in the direction of the arrows;

Fig. 20 is an enlarged sectional view taken substantiaily in the plane of the line 2li- 20 of Fig. 17;

Fig. 21 is a sectional view taken substantially in the plane of the line 2i--2i of Fig. 17, parts being omitted and the fluid pressure mechanism 35 being shown somewhat diagrammatically;

Fig. 22 is a view in elevation of a distributor block shown in Figs. 4, 17 and 2l.;

Fig. 23 is an enlarged sectional view of iiuid pressure regulating valve mechanism of Fig. 21 and taken substantially in the plane of the line 23-23 of Fig. 24; Y,

Fig. 24 is a sectional view taken substantially in the plane of the line 2li-2t of Fig. 23.

General description In the specific embodiment of the invention herein illustrated, 5 indicates the main frame of the machine which preferably carries all of the operative mechanism. The primary driving 50 means is illustrated as a motor 6 mounted upon .the frame 5 and having a. shaft 1 extending into the power unit casing 8 also mounted upon the frame. `Through suitable gearing mounted in and :upon the casing t, power is transmitted from the 55 motor to the spindles and to the feed mechanism, indexing, locking and control mechanism.

The turret (in this case a spindle carrier 9) is mounted upon or forms a part of central stem means I8 (Figs. 4 and 5) supported in spaced bearings upon the frame. Spindles II-II are carried by the turret or spindle carrier and are revolved by a chain I2. The spindles preferably carry chucks while tools are carried by a tool carrier or slide I3 slidable upon one stem portion. Cross tool carriers (Figs. 2 and 5) are carried by substantially supported shafts and are actuated by cams. The tool slide. I3 is fed by a draw rod I5 preferably extending centrally through the central stem portions I8 to the head end of the machine where it is actuated by the main cam I6 driven from the power unit.

The main cam shaft I1 carrying the main feedA cam I6 is suitably geared to secondary or auxiliary cam shafts and all automatic control mechanism is primarily actuated from said main cam shaft I1.

'Ihe chucks carried by the spindles II may be actuated by pressure fluid, preferably oil, by means more specifically shown in Figs. 17 to 23, and all chucks holding work in operating positions are assured of a constant adequate supply of pressure fluid. Various features of the invention in the form herein illustrated will now be described in detail.

Power unit The power unit heretofore referred to is shown more in detail in Figs. 11, 12, 13 and 14. The case 8, as stated, is mounted upon the main frame 5. The primary driving shaft, 'or specifically the motor shaft 1, extends into the casing for driving the speed and feed gearing and may continue through the opposite side of the casing 8 for directly driving the fluid pressure pump I8 mounted upon the outside of the case 8.

The shaft 1 within the case 8 is provided with worm means specifically shown as two worms I S-ZI'L The worm I9 drives the fast traverse while the worm 20 is the initial drive for the slow traverse and the spindles. The worm I9 meshes with and drives a worm wheel 2| freely mounted as by means of an antifriction bearing 22 upon a shaft 23. The shaft 23 is adequately supported in spaced bearings 24-25 carried respectively by an upstanding web 26 and the side of the casing 9. The shaft 23 carries a clutch member 21 splined thereto and having engaging means such as teeth to coact with complementary clutch means of the worm wheel 2l, as will be clear from Fig. 12. The clutch member 21 is. actuated by a yoke 28 carried by an arm 29 which itself is carried by a shaft 38 actuated by a segment 3l and rack 32,

'as will be described more in detail in connection with the feed and control mechanism. 'I'he shaft 23 carries a bevelgear 33 meshing with a bevel gear 34, which gear 34 is non-rotatably secured to the main feed cam shaft 35.

When the clutch member 21 is thrown in, the worm wheel 2l drives the shaft 23, and through the meshing bevel gears 33-34, the main feed cam shaft 35 is driven at the appropriate speed to be determined by the various functional characteristics of the machine. Ordinarily, this speed will be the fastest speed imparted to the feed drive cam shaft 35 and is the fast traverse which is employed for retracting the tools, indexing the turret or spindle carrier, and jumping the tools back to operative position. When the clutch member 21 is thrown out. the worm. wheel 2l merely idles upon the shaft 23, and if the shaft 35 is beingA mounted in a bearing 38 in the upstanding web 26- and in an opposite bearing 39 in the casing 8. The shaft 31 extends through the casing 8 and at the outer end carries a gear 4U on the outside of the casing. A second gear 4I meshes with the gear 40 and is carried by a shaft 42 extending into and through the' casing 8. The shaft 42 is the spindle drive shaft and at the end opposite the gear 4I is connected to the spindle driving means (in this case the chain sprocket), as will be later described. The gears 40-4I are pick olf gears so that by substituting other gears the speed of the spindle drive shaft 42 may be varied so as to give. the desired spindle speeds.

In the form illustrated, the spindle drive shaft 42 is in the train of gearing constituting the slow traverse. The spindle drive shaft 42 carries a. worm 43 which meshes with a worm wheel 44 carried upon a stub shaft 45 extending tothe outside of the casing 8. A pick off gear 46 is mounted upon and driven by the shaft 45. A second pick olf gear 41 meshes with the gear 46 and is mounted upon a shaft 48 extending downwardly into the casing for ultimately driving the shaft 35 at the slow traverse speed. The shaft 48 drives the main feed shaft 35 through an overrunning clutch or ratchet mechanism, as will be described, so that when the fast and slow traverse are both in, the fast traverse will be able to drive, and the overrunning clutch will merely ratchet.

In the form illustrated, the shaft 48 has a clutch member 49 splined thereto. 'Ihe clutch member 49 is actuated by a yoke 50 on a shaft 5I, which shaft also carries an arm 52 at'k the outside of the casing 8 and may be actuated through a. link 53 and arm 54 as will be later described in connection with the feed and control mechanism. The clutch member 49 is designed to coact with a complementary clutch member 55 carried upon a hub 56 which at the lower end carries one member 51 of an overrunning' clutch. This overrunning clutch may be of any desirable form and 'as illustrated the member 51 may be a scalloped plate carrying balls or rollers 58-58 which seat in suitable recesses formed in the lower hub portion of the bevel gear member 34. Thus, when the clutch members 49-55 are in engagement and the fast traverse clutch is thrown out, the ratchet member 51 will drive the main drive shaft 35 through the clutching or ratchet elements 58. It will be seen that by reason of the two pairs of pick oil' gears lill-4I and 46-41, the spindle speeds may be varied and the slow traverse speed' likewise varied so as to give the desired speed and slow traverse feed.

'I'he gearing within the housing 8 preferably operates in grease or oil and all interior parts are accessible when the cover member 59 is removed. The gears l0-4l are preferably enclosed by a removable cover 68 (Fig. 3), and the gears IS-41 are preferably likewise housed under a removable cover 6I. By mounting the oil pump I8 directly Turret and operation The turret (see Figs. 4 to 10) (in this case a spindle carrier 9) is mounted upon the frame so as to be indexed with great ease and yet held in indexed position with great accuracy and rigidity. The carrier such as the turret 9 has projecting stem portions, either or both of which may or may not be integral portions of the turret. In the illustrated form, the turret 9 is a separate member mounted upon the separate central shaft or stem member l0. The rear end of the carrier 9 abuts .a shoulder 62 in the stem (Figs. 4 and 17), to prevent endwise movement of the spindle carrier thereon. The stem portions Ill projecting from the spindle carrier (whether formed integrally therewith or as a separate member or members) will preferably be of heavy construction and supported at one end in a substantial frame bearing 63 carrying antifriction bearings SI1- 65. The two antifriction bearings are preferably initially loaded and the bearing 65 resists end thrusts toward the left set up by the tools during operation. The stem portion projecting at the right hand end (Fig. 5) is mounted in a substantial frame bearing 66 embodying antifriction bearings 61-68. These bearings, if desired, may be floating so as to provide for the limited longitudinal expansion and contraction of the stern means without affecting the bearings 6ft- 65 and yet afford the right hand stem portion the substantial support which is desired. A

During indexing movements of the spindle carrier and stem I0, the latter preferably is the sole bearing support for the spindle carrier; that is to say, the spindle carrier is out of bearing contact with the main frame. This construction permits an almost frictionless indexing, and indexing may be at a rapid rate. Between indexing movements, the turret is rigidly supported from the frame so as to denitely hold the. tur` ret against movement in any direction and permit work of great accuracy to be turned out.

The indexing of the turret may be performed by any suitable mechanism, but preferably we employ a Geneva type of index which may include slotted members 69-69 (Figs. 4 and 6) to be engaged by a roller 1D carried upon the Geneva arm 1| fixed to the main cam shaft |1 so as to be rotatable therewith. Thus, as will be readily understood, when the cam shaft |1 carrying they arm 1| is rotated, the roller 10 will engage the slotted members 69 and index the turret step by step in a well known manner.

As has been heretofore stated, during indexing movement of the turret the latter is preferably supported solely by the stem I0 and the. end bearings. At each work station, however, the carrier is preferably solidly engaged with a part of the frame so as to rigidly support the carrier and prevent movement or vibration. In the form shown (Figs. 7 to 10), the forward web 12 of the turret or spindle carrier is provided with one circumferential series of locking grooves or notches 13 equal in number to the numberlof indexed positions of the carrier. These locking grooves or notches are preferably formed in hardened steel blocks 14 set into the turretweb 12 and are provided at one side with a radially extending surface 15 andy at the opposite side with an inclined surface 16 serving'as a cam surface. In line with the series of notches 13 is a locking arm 11 pivotally mounted upon a shaft or pin 18 carried by the main frame 5. This locking arm is provided with a surface 19 to t flat against the radial surface 15 when the arm is in the in position shown in Figs. 7 and 10. A moderately heavy plate spring serves to constantly urge the locking arm 11 in the locking direction. With the locking arm in the in position and the two surfaces 15-19 both extending radially of the turret, there is no tendency for the arm 11 to be cammed out so long as these surfaces are in Contact and the turret will be rigidly held against rotative movement in one direction. When the turret is moved in the indexing direction, that is, counterclockwise, as viewed in Fig. '1, the cam surface 16 engages the corresponding cam surface 8| opposite the surface 19, and the locking arm is cammed out and overcomes the tendency of the spring 80 to hold the same inwardly. Between indexed positions, the nose of the arm 11 rides upon the outside of the web 12 until the next notch 13 arrives in position when the arm is again forced in by the spring 80 and locks the 'carrier against rotation in one direction.

The web 12 may also be provided with a second set of locking grooves or notches 82 preferably in longitudinal alignment with, but spaced from, ,the series of notches 13. The locking grooves 82 are also preferably formed in hardened steel blocks 83 set into the circumference of the web 12. Each notch 82 is provided with a cam locking surface 8d to be engaged by a cam locking surface 85 on a locking arm 86 pivotally mounted on a shaft or pin 81 carried by the frame at the side opposite the arm 11. A very heavy plate spring 88 engages the arm 96 and urges the same in- Wardly into the locking notches 82 successively. Due to the strength of the heavy spring 88, it is not usually practicable to have the arm 86 Cammed out of the notches 82 by the indexing movement of the turret and we preferably provide mechanical means for moving the arm 86 out of locking engagement with the turret. In the form shown, the lower free end 89 of the arm 86 is positioned to be engaged by the end 90 of a lever 9| mounted for oscillation upon a shaft or pin 92 in the frame. The free end of the lever 9| may carry a roller 93 to be engaged by a cam 96 upon the main cam shaft |1. Thus, when the camshaft |1 is rotated, the lever 9| is rocked to remove the nose of the arm 86 from the notch 82, and the arm 85 is held in the out position by the dwell of the cam 94 while the turret is being indexed. As soon as the turret has reached its indexed position, the arm 11 is forced in as heretofore described, and the roller 93 on the lever 9| leaves the cam 94, and the heavy spring 88 forces the nose of the lever 86 into the notch 82. The cam surfaces 84--85 contacting with each other tend to force the turret downwardly and cause the arm 11 to lock more tightly. This tendency ofthe arm 86 to cam or force the turret downwardly is taken advantage of by us for providing a rigid support for the turret between indexing movements.A

We preferably provide adjustable means to be engaged by the turret only when the turret has been indexed and the locking arms 11-86 move the turret downwardly a slight permissible dis--y tance. In the form shown, we provide one or more adjustable supports 95-95 (Fig. 7) beneath the turret. These supports 95-95 maybe in the form of pins beveled off so as to substantially fit the circumference of the web 12. These supports or pins may be moved inwardly for adjustment by means such as screws 96-96 in the frame. By -means of the screws very nice adjustments may be made, and the supports 95-95 i tion employed, the sprockets are suitably held positioned so as to be just out of bearing contact with the turret during indexing movements. When the turret is indexed and the locking arms 11-86 are in engagement with the turret, the very slight give in the stem meansl I0 will permit the turret to be moved into tight supporting engagement with the supports 95-95. It is to be understood that this movement transversely of the stem axis is exceedingly slight, but even the slightest spacing of the spindle carrier from the supports 95-95 will permit indexing with the greatest ease, and yet when the turret is drawn down into supporting bearing engagement with the supports 95-95, the turret will be held with great rigidity and the frictional holding forces of the supports just mentioned will relieve the .thrust bearing of the central stem |0 of some of the thrust load created by the tool pressures during operation.

In order to prevent chips and the like from passing between the hood portion 91 of the frame 5 and the spindle carrier 9, we may provide a felt or other dust ring 98 (Figs. 5 and 17) seated in a counterbore 99 (Fig. 8) and held therein by means of retaining rings |00 secured to the face of the hood portion 91 as by means of screws |0|-|0|., The felt ring 98 constantly bearing upon the spindle carrier will prevent chips from working between the turret and the hood portion of the frame.

Spindles and drive As shown more particularly in Figs. 4, 5, 15 and 17, the spindle carrier or turret carries a number of chucking devices, in this case in the form of ,rotary spindles provided with chucks at the front end and driving means at the rear end. In the form illustrated, each spindle is mounted in antifriction bearings |02|02 of ample proportions in the front web 12 of the turret. Rear bearings ID3-|03, which may be smaller than the forward bearings, support the rear end of each spindle in the rear web |04 of the turret. In the bearings |02-I02, which are initially loaded, the outer rings are flxedly held in a counterbore in the web 12 by means of an annular ring |05 secured as by means of screws |06 to the turret web 12. The inner rings are held between a shoulder |01 on the spindle and a nut |08 threaded thereon. The rear supporting bearings |03 may be oating. .Each ring |05 may carry a sealing ring |09 of felt or the like bearing on the forward end of the spindle Il. Each spindle carries a chuck |I0 of desired form.

The spindles are driven, in the form shown by means of a chain and the driving system is of novel form. The rear end of each spindle is provided with a sprocket secured thereto.

In the form of machine illustrated wherein hydraulic chucking devices are employed, a fluid pressure cylinder YI|2 may be directly keyed to the spindle at ||3 and the sprocket keyed to the projecting sleeve of the cylinder ||2 as lndicated at'||4. Whatever the specific constructo the spindles so as to drive the same. As heretofore described, the spindle drive shaft 42 (Fig.' 11) is driven at the selectedpredetermined speed. The shaft 42 (Figs. l1, 15 and 16) is supported at the forward end in a bearing ||5 in a bracket IIB, which may be secured to a main frame or the housing portion 91 thereof. BetweenA the bearing H5 and the power unit, the spindle drive shaft 42 carries a driving sprocket i! l1 over which the driving chain I2 is trained.

.fluid through the pipe As will be clear particularly from Figs. 3, 15 and 16, the driving sprocket ||1 is arranged outside of the circumferential path of the spindles for a purpose to be described, The chain I2 is trained over the spindle sprockets I I-I I and is in constant driving contact with all of said spindle sprockets except one which is in the loading position. The mounting of the driving sprocket I|1 outside of the circumferential path of the spindle sprockets permits one spindle sprocket to leave driving contact with the chain during each indexing movement and causes the spindle sprocket which was in the loading position and therefore out of driving contact with the chain,

to again be moved into driving contact with the chain' upon each indexing -,movement of the spindle carrier. By means of the arrangement shown, one spindle is always automatically uncoupled from the driving ,chain upon each ndexing movement of the spindle carrier, and this uncoupling is permitted without the use of clutches and attendant operating mechanism.

In order to take up slack in the chain I2 when one spindle sprocket is leaving contact with the chain and when another sprocket is moved into engaging contact with the chain, we prefer to provide a chain tightener. In the form shown, the bracket IIB carries a lever IIS pivotally mounted thereon at I|9. One end of the lever carries a roller |20 for engagement with the chain, while the other end of the lever is moved by suitable means to urge the roller into contact with the chain and keep thel latter taut. In the form shown, we employ a fluid pressure cylinder I2I carried by the bracket IIB, which cylinder carries a plunger |22 for engaging the end |23 of the lever IIB. The cylinder |2| is in constant communication with a source of pressure |24. If desired, a set screw or the like |25 ,may be employed for limiting the inward movement of the end |23 of the lever ||8. The chain drive and adjacent parts are preferably enclosed beneath a suitable hoody as shown more particularly in Figs. 1, 2 and 3, so as to exclude foreign matter and prevent splashing of lubricant.

Tool carriers As heretofore described, the work carrier is supported and held with great rigidity, and the tool carriers to be described are likewise rigidly supported so as to permit the turning out of work of a. high degree of accuracy. In the form shown (Figs. 1, 2 and 5), the main tool carrier is in the form of a slide I3 accurately tting and A slidable upon the supporting stem I0. The slide I3 may have a plurality of flat sides provided with slots |21 for securing tool holders to the slide. The slide may be reciprocated by means of the actuating or draw rod I5 as will be described.

In the form shown, the rear end of the slide I3 is provided with a seat to be received within a ring or bearing portion |28 on a rear enclosing hood |29 extending outside of and over the bearings 61-68 of the stem |0 and serving to protect such bearing, as well as the adjacent parts of th supporting stem I0, from chips and dirt. The hood |29 may be dowelled or otherwise rigidly secured to the tool slide as indicated at |30-|30. The lower side of the hood |29 is open so as .'.o straddle the upstanding portion |3| of that part of the frame carrying the bearing housing 66. The upstanding frame portion I3! preferably carries hardened steel bearing blocks |32|32 at opposite sides, which blocks are engaged by finished bearing surfaces |33- |33 on the downwardly extending skirt portions of the hood |29. Thus, when the slide I3 is reciprocated, it is accurately guided in a longitudinal direction by the hardened steel wear blocks |32-I32 and the coacting slide surfaces |33 on the hood. This construction provides a very rigid support for the slide against any rotative movement. l

The rear end of the hood |29 at the outside of the frame is closed by a substantial end cap |34 secured thereto as by means of screws |35-|35. The actuating or draw rod I5 passing centrally through the bore in the supporting stem I is secured to the cap |34 as by means of a cross in |36. Thus, when the draw rod I is reciprocated by the main cam I6 as will be later described, the tool slide I3 is reclprocated longitudinally and during such reciprocating is solidly supported against any rotative movement and is accurately guided longitudinally by the stem I0. The forward end of the slide I3 may carryl a dust ring |31 of felt or the like for excluding chips and other foreign matter from the wear surfaces between the stem |0 and slide I3. At

the rear end ofthe slidev I3 such a dustring may be omitted since that end of the slide is adequately protected by the hood |29. An inner portion of the slide I3 may be chambered as'shown at |38` (Fig. 5) so as to hold a supply of lubricant entering through a radial hole- |39 in the stem |II. y

We may employ tool carriers in addition to the tool slide I3. In the form shown, onlyr two additional tool carriers or forming tool supports are shown, which, in the particular form illustrated, are oscillating carriers I40--I4I (Figs. 2 and 5) mounted upon substantial shafts |42- |43 supported in bearings I 44-I45 in the frame 5. These substantial shafts |42|43 provide a very rigid support for the oscillating tool carriers so as to prevent chatter. The oscillating tool carriers are actuated by cams |46| 41 carried by the auxiliary cam shafts I 48-I49 respectively (Figs. 2, 4 and 6), which shafts are journaled in the frame,as will be understood. Clearly, any practicable number ofoscillating or cross `slide tool carriers may be employed, as will be understood by those skilled in the art.

Feed mechanism and controls As heretofore explained, power is transmitted through the power unit (Figs. 11 to 13) either by the fast or slow traverse gearing to the shaft 35 which drives the main cam shaft I1. All of the feed mechanism, as well as unlocking and locking of the spindle carrier, indexing, etc., are timed by the main cam shaft I1. In the form shown, the .main feed shaft 35 is provided with a worm |50 and is mounted at the bottom in a bearing |5I carried by the frame' 5. The worm |56 meshes with a worm-wheel |52, Fig. 4, mounted so as to rotate the main cam shaft I1 and the cam drum I6. The drum I6 is provided with' cam means such as the cam groove |53 which receives a cam follower |54 carried by a, follower slide |55 slidable in ways such as |56 on the main frame. The feed slide, draw rod I5 is secured to the slide |55 as by means of aypin |51 so that upon actuation of the slide Vby the cam |53, the draw rod I5 will be actuated so as to reciprocate the. main tool side I3. The thrust of the cam drum |6 may be taken byV athrust bearing |58 mounted between the web |59 and a part of the cam drum or other part carried by the cam shaft I1. The main cam shaft I1 as heretofore described carries the indexing ,arm 1| for indexing the turret or spindle carrier and also carries the cam 94 for withdrawing the locking arm 86 as heretofore described.

The main cam shaft I1 in the form shown is geared to and drives the auxiliary cam shafts |48-I49 (Fig. 6) mounted in suitable bearings in the web |59 and the web |60 (Fig. 4) on the frame. The shaft I1 carries a spul` gear |6| which meshes with a spur gear |62 on the auxiliary cam shaft |48 and with a spur gear |63 carried by the auxiliary cam shaft |49. The gears |6I, |62 and |63 are preferably of the same size so that for each revolution of the main cam shaft I1 there will be one revolution of each of the auxiliary cam shafts Idil-|49. The auxiliary cam shaft, |49 as heretofore noted carries a, cam |41 for engagement with the roller |64 on the arm for swinging the rear oscillating tool carrier |4|. 'Ihe auxiliary cam shaft |48 as heretofore noted carries the cam |46 for engaging the roller |65 for similarly actuating the fr ont Oscillating tool carrier |40. The cams heretofore referred to are so timed that when the tool slide I3 is in operating position and when the oscillating slides are in active position the turret is locked. When the tool carriers are withdrawn to inactive position, the cam 94 unlocks the turret, and the indexing arm 1| indexes the same. The shafts |48, |49 are preferably in a horizontal plane below the shaft I1. The shafts |48, |49 are thus positioned adjacent the front and back sides of the fra-me where they are readily accessible for cam changing. The cams are preferably longitudinally rearwardly of the generally upstanding transverse frame wall forming a bearing for the front of the spindle carrier (Fig. 5),;

In addition to the actuation of the tool carriers, unlocking of the turret, indexing, etc., controlledby the cam shafts, We provide additional cams for controlling the fast and slow traverse and for stopping the machine when desired at the end of each cycle. In the form shown, such additional cams are carried by, drums on the front auxiliary cam shaft I 48, as will be described.

`The rack bar 32 (Figs. 11 to 14) as has been noted is employed for actuating the fast traverse clutch member 21 for throwing the fast traverse in and out. 'This rack bar 32 may be `actuated manually and automatically. As herein illustrated, the rack bar 32 extends through the power unit casing 8 and is guided in a bearing bracket |66 on the frame (Fig. 11). The end of the rack bar 32 adjacent the bracket |66 is provided with rack teeth for engagment with a pinion |61 rotatably mounted f handle |14 is connected to the hollow shaft |13 so that upon swinging of the handle I 14 the pinion |12 will move the rack bar |69 and through .the pinion |61 the horizontal rack bar 32 will be moved so as to throw the fast traverse clutch part 21 in orout. In the preferred form, the hollow shaft |13 carrying the pinion |12 extends through the frame and is provided at the rear side thereof with an actuating handle |15 (Figs. 2 and 3) similar to the handle |14 at the front. Thus, an operator at either the front or the back side of the machine may actuate thefast traverse clutch manually.

We provide means for hand-cranking of the machine for setting up, etc., and provide locking mechanism whereby when the hand-cranking mechanism is thrown in, the fast traverse is locked out so as to avoid injury to the operator. In the form shown (Figs. 1, 2, 3 and 11), a handcrank |16 is carried by a shaft `|11 which may pass through the tubular shaft |13 carrying the handles |14-| 15. The shaft |11 carries a bevel pinion |18 meshing with a bevel pinion |19 on a vertical shaft |80. At the upper end, the shaft |80 carries a bevel pinion |8| to be engaged at times by a bevel pinion |82 on a sleeve shaft |83 slidable in the frame. The shaft |83 may be spring pressed rearwardly as by means of a spring |84 interposed between a collar on the end of the shaft and a bracket carried by the frame, as will be clear from Fig. 11. Splined to the sleeve shaft |83 is a shaft |85 passing into Vthe power unit casing 8 and carrying a bevel pinion |86 meshing with a bevel pinion |81 on a shaft |88 within the casing 8 (Fig. 13). The end of the shaft |88 carries a bevel gear |89 meshing with a bevel gear |90, which may be formed inte- A grally with the hub 9| which carries the fast traverse bevel gear 34. Thus, the .main cam drive shaft 35 may be hand operated by the crank |18 or the duplicate hand-crank |92 carried by the other end of the shaft |11 extending through the frame.

When the machine is to be hand-cranked, the fast traverse clutch is thrown out and the sleeve shaft |83 is moved toward the left as viewed in Fig. 11 to engage the bevel gears |8||82. The short handle |93 is then turned so as to bring the latch |94 carried thereby into position behind the collar of the bevel gear |82 so as to hold the gears |8||82 in engagemenfwith each other. Then, upon rotation of either of the cranks |16-|92, the shaft |80 will be rotated through the bevel gears |18|19 and the shafts shaft |83, which detent will be in position beneath the abutment |96 carried by the vertical rack rod |69 so that the latter cannot be moved downwardly by the handle |14 or |15 to throw in the fast traverse clutch. It is only when the gears |8||82 are out of driving engagement with each other that the fast traverse handles |14-I15 can be moved to throw in the fast traverse clutch part 21.

The slow traverse clutch 49 (Figs. 11 to 13) ancbarm 54 carried by the shaft |91 extending .across the frame and journaled in a bracket on the casing 8. 'I'he shaft |91 carries a manual actuating handle |98 at the rear side of .he machine and carries an actuating lever arm |99 at antenas the forward side of the machine. Thus, by moving the handle |98 at the rear of the machine,

the slow traverse clutch member 49 may be thrown in or out. At the front of .the machine, we preferably provide a slightly different arrangement for manually throwing the slow traverse clutch. In the form illustrated, the actuating arm |99 is pivoted to a vertical bar 200 slidable in bearings on the frame. A spring 20| positioned beneath a collar 202 on the vertical bar 200 urges the bar 200 upwardly and the clutch 49 to the clutched in position. The bar 200 carries a collar 203 rotatably mounted on the bar 200 and interposed between collars 204-205 on the bar 200. A spring 206 normally tends to hold the collar 203 in the elevated position on the bar shown in Fig. 11. The collar 283 has a handle or hand grip 201 which may be manually actuated'for throwing the slow traverse clutch 49 in or out, as will be clear. The spring 20|, as heretofore stated, normally tends to hold the slow traverse clutch 49 in the clutched in position. When it is desired to hold the clutch 49 in unclutchedposition, the handle 201 is depressed so as to throw the slow traverse clutch 49 out, and then by means of the handle 201 the collar 203 carrying a detent finger 208 (Fig. 3) is rotated so as to move the latter beneath an abutment 209 carried by the frame. The detent and abutment will then hold the slow traverse clutch in unclutched position.

In addition to the manual means described-for throwing the fast and slow traverse clutches, we provide means for automatically throwing the fast traverse clutch at times and preferably for throwing the slow traverse clutch when the machine is arranged for hand loading and the machine stopped at the end of eachl cycle. For magazine feeding the machine would not ordinarily be stopped at the end of each cycle, but would continue in operation until manually stopped.

In the form shown, the traverse. clutches 21-49 are automatically actuated by cam means on the auxiliary cam shaft |48. If we assume the main feed cam I6 to be in the position shown in Figs. 4 and 11,-the main tool slide 3 will be at substantially the inner limit of its travel, and we shall assume that during the feed movement the cam i6 has been actuated by the slow traverse. Assuming that the cross tools have nished their operations, it is desirable to throw in the fast traverse for retracting the tools and indexing the turret. It may be desirable, though not necessary, to throw out the slow traverse when the fast traverse is-in. In order to automatically throw out the slow traverse, we may provide a cam such as 2|0 carried by a small cam drum 2H on the auxiliary cam shaft |48. The cam 2| 0- is properly positioned circumferentially so that at the proper time it engages the roller 2|2 carried by the arm 2|3 on a shaft 2I4 journaled in the frame. The shaft 2|4 carries an arm 2|5 pivotally connected to the lower end of the vertical bar 200. When the cam 2| 0 engages the roller 2 I2, the bar 200 is moved downwardly against the spring 20| and the slow traverse clutch is thrown out. As soon as the cam 2|0 has passed from behind the roller 2|2, the spring 20| again throws in the slow traverse clutch. In the machine as herein illustrated, the single cam 2|0 is positioned to throw out the slow traverse clutch only at the end of each cycle. Y

The fast traverse clutch part 21 (Fig. 12) is thrown in by a cam 2| 6 (Fig. 11) carried upon a drum 2|1 on vthe auxiliary cam shaft |48. The cam 2|6 is adapted to engage a roller 2|8 on an arm 2|9 carried by a shaft 220 journaled in the frame. In the form shown, a plate spring 22| is connected so as to move with the shaft 220 upon oscillation thereof by the cam 2|6 or other cams. The spring 22| is operatively connected to the rack bar |69 as by means `of a notch 222 in the bar |69 into which the end ofthe spring 22| extends. Thus, when the cam 2|6 engages the roller 2|8, the shaft 229 is oscillated in its bearings and the spring 22|, which is of sufiicient stiffness, moves the rack bar |69 downwardly so as to throw in the fast traverse clutch 21 the same as if the bar |69 had been moved downwardly by either of the manual handles |14 or |15 as heretofore described. If while the roller 2|8 is in engagement with the cam 2|6 it is desired to throw out the fast traverse clutch manually, the spring connection 22| will permit this to be done. It will be clear that with the spring 22| `property proportioned, such spring will be strong enough to throw in the fast traverse clutch by means of the cam 2|6, but the spring may be exed sufficiently to throw the fast traverse clutch out manually by means of the handle |14 or |15. When'the tools have been retracted and the turretindexed, the fast traverse clutch 21 is thrown out. For the purpose of throwing the fast traverse clutch out, we provide a cam 223 to engage the roller 2| 8 so that the shaft 220 will be rocked andthrough the spring 22| the fast traverse clutch will be thrown out. The slow traverse clutch 49, if not previously thrown out by the cam 2|0, is thrown out at the time the fast traverse clutch is thrown out by the cam 223. The feed mechanism will then be stopped and the chuck in the loading position is loaded. The operator then manually moves the handle |14 or I|15 to throw in the fast traverse clutch 21, this throwing in being permitted by the spring 22| even though the roller 2 |8 is still in engagement with the cam 223. With the fast traverse clutch in, the tools will be jumped to operative position, and then anothercam 224 similar to the cam 223 will engage the roller 2|8 for throwing out the fast means of screws 221 (Fig. 15).

traverse clutch and previously the slow traverse throw out cam 216 will have released the cam roller 212 and the slow traverse clutch 49 will have been thrown in so that the cam drum I6 will be driven through the slow traverse gearing for feeding the tools.

Fluid pressure chuclcing system The chucking devices may be actuated by fluid pressure means.

-the,passage 229 leads to the head end whereby pressure fluid may pass to and exhaust from either end of the cylinder at appropriate times, as will be described. The tail end passage 223 is in constant open communication with an annular passage 239 (Fig. 19) in the cylinder head In the form shown, the rjaws of each chuck ||9 (Fig. 17) are actuated 226, and the head end passage 229 is in constant communication with a second annular passage 23| in the cylinder head.

Each cylinder head is rotatably connected to a ring member 232 which has a running fit with what may be termed a distributorv block 233 (Fig. 22). The ring member 232 may be connected to each cylinder head by means of a bolt 234 secured to the cylinder head and passing through an aperture 235 in the ring. An antifriction bearing 236 may be employed for permitting free rotation of the bolt 234 and cylinder head 226 while still maintaining a relatively close running t between the ring 232 and each cylinder head. The ring 232 adjacent each cylinder has a passage 231 in constant communication with the tail end passages 228-230 in the cylinder. The ring 232 is also provided with a second passage 238 in constant communication with the head end passage 229--23I of each cylinder.

The distributor block 233 has an outwardly opening circumferential uid passage or groove 239 extendingx in the form shown, about twothirds of the Way around the circumference.

This passage 239 is in line with the passage 238 in the ring 233. The distributor block 233 has a second passage 240 in line with but entirely separate from the passage 239. The distributor block 233 has another passage 24| extending circumferentially but out of line with the passages 239-240. In the form illustrated, the distributor block 233 is non-rotatably secured to a part of the frame such as that part 63 carrying the bearings 64-65 for the stem Ill. A passage 242 (Fig. 21) leads from a source of pressure fluid into the extended passage 239. A second passage 243 leads to the passage 240 in the distributor block, while a third passage 244 leads to the passage 24| of the distributor block. The passage 242, and consequently the extended passage 239 of the distributor ring, is designed to be in constant communication with asource of high pressure fluid so as to maintain all of the chucks, except the one in loading position, in closed position, as will be described. The passages 243-244, and consequently the passages 24U-24|, are designed to be alternately connected with exhaust and with a source of pressure fluid for reciprocating each piston for opening and closing the chucks in loading position as will later appear.

the extended passage 239 or the passage 240, depending upon the circumferential indexed position of the ring 232, while the passage 238 is designed to communicate only with the passage 24| for' a purpose to be described.

' While the passages in the cylinder head ring 232 and distributor block 233 may receive pressure fluid from any suitable source, we prefer to 'Ihe passage 231 in the ring 232 is in such positon as to communicate with employ oil as the pressure fluid and have devised a particularly advantageous and novel supply system which will now be described. The pump IB of any desirable type isV driven as by means of a direct connection with the motor shaft as heretofore described. The intake 245 (Fig. 21) receives lluvid through a strainer 246 in the sump in a suitable chamber 241 (Figs. 4 and 5) in the frame of the machine; The discharge pipe 248 from the pump I8 delivers fluid through the pipe 249 directly to the passage 242 and consequently to the extended interior fluid passage 239 in the distributor lring 233. A branch lineA |24 delivers pressure fluid directly to the belt tightener device` shown in Fig. 16 when such device is em- `pressure fluid so that the piston in cylinder ||2 in loading position is actuated by pressure fluid stored up by the pump so that the direct pump pressure is not reduced by the sudden rush of uid for reciprocating the piston, and consequently the chucks which are in working position are constantly maintained closed.

In the form illustrated, the discharge pipe 248 having branches 249 andn |24 (the latter when required) delivers pressure huid to a passage 250 (Figs. 23 and 24) in what may be termed a valve block 25| mounted on the frame of the machine. The fluid in passage 250 in order to pass therethrough must build up to a sufcient pressure to raise the valve plug 252 tting in the seat 253. An adjustable spring 254 urges the valve plug 252 downwardly so that by adjusting the spring 254 by means of the screw plug 255 it is possible to adjust the pressure at which the valve plug 252 will be moved to open position as shown. in Fig. 23. Thus, before the plug 252 opens the passage, the pressure in the discharge line 248 and consequently in the communicating branch line 249 must build up to at least the pressure determined by the adjustment of i the spring 254. From the passage 250 and valve passage 253, the pressure fluid passes through a transverse passage 256, through passage 251 fitting 258 (Fig. 21), and into the accumulator or vair bell chamber 259. A passage 260 formed in the valve block permits uid to pass either from the accumulator or directly from the passage 256 to a passage 26| communicating with a pipe 262 which leads to the manual or other control valve 263 fr a purpose to be described. An air cushion in the chamber 259 permits a storage of a considerable quantity ofv fluid underpressure, which uid is available for reciprocation of the piston and draw rod controlling the chuck in loading position. When a predetermined pressure has been built up in the accumulator chamber 259, excess fluid Aentering through the pipe 248 serves to build up pressure in the passager 260 and valve passage 264 so as to raise the relief valve plug 265 against the spring 266. The spring 266, by means of the plug 261, may be set to permit the valve plug 265 to open at any predetermined pressure. Such excess pressure fluidthen passes through the passage 268, passage 269, and pipe 216, either back to the sump or preferably to such points as desired where it may discharge and spill over certain working parts for lubricating the same. It is desirable that this excess fluid from the pressure relief line 210 should discharge over such working parts as are above or in communication with the sump chamber 241 in the main frame so that all excess fluid will be drained to the Sump.

As stated, the pipe 262, which is in open communication with the accumulator chamber 259, is connected to the control valve 263. From the control valve 263, a pipe 21| leads to the passage 243 which in turn communicates with the short circumferential passage 240 in the distributor block 233 which passage is in line with the extended passage 239 as heretofore described. Another pipe 212 communicates with the valve 263 ployed. It will thus'be seen that the direct pump and with the passage 244 which in turn communicates with the offset circumferential passage 24| in the distributor block 233. Anotherpipe 213 leads from the control valve 263 and communicates either directly with the sump or leads exhaust uid from the valve to a point Where it is spilled overvworking parts to be lubricated as heretofore described in connection ,with the relief pipe 210.

The operation of the hydraulic chucking system is as follows:

When the pump |8 is started, fluid pressure builds up in the discharge line 248 and direct connected branch line 249, which, as stated, ultimately communicates with the extended passage 239 in the distributor block 233. The passage 239 is of such extent and is positioned circumferentially so that the passages such as 231 (Fig. 18) in the ringA 232 corresponding to each of the cylinders, except the, one in the loading position, will be under high uid pressure, and such uid pressure will be transmitted to the tail end of the cylinders ||2 and al1 of the chucks (except that in the loading position) will be maintained closed. When the turret indexes so as to bring one chuck each time into the loading position (Fig. 15), the passage 231 inthe ring 232 will leave communication with the extended passage 239 and will then pass over the ungrooved portion of the distributor block 233 and will finally be stopped in the loading position with the passage 231 in communication with the short circumferential passage 240. This passage, it will be remembered, is in communication with the passage 243 and pipe 21|. Theother passage 238 (of the cylinder in loading station) leading to the head end of the cylinder will then be in communication with the short circumferential passage 24| which, as heretofore described, is in communication with thepassage 244 and pipe 212`. Thus, with the control valve in the position shown in Fig. 2l, the fluid in the tail end of the cylinder may escape through passage 231, passages 249-243, and pipe 21|, through the valve 263 and into the exhaust pipe 213. At the same time, pressure fluid from the accumulator chamber 259 will pass through pipe 262, valve 263, into pipe 212, through passage 244, passage 24|, and into passage 236, and thence to passage 229 (Fig. 17) into the head end of the cylinder in loading position so as to move the draw rod 225 forwardly to open the chuck.r

A new work-piece may then be inserted in -the chuck and the Valve 263 moved to opposite position so asto cause the pipe 262 to communicate with pipe 21| passage 243, passage 24|), passage 238 and cylinder passage 228 and the tail end of the cylinder to again close the chuck. During this closing movement, the passage 24| communicating with the head end of the cylinder will be in communication through passage 244, pipe 212, and valve 263, with the exhaust pipe 213. After the chuck has been closed, the turret again indexes to cause the chuck which has just been closed to again index into working position and be driven by the chain as heretofore described. During indexing of the lately closed chuck, the passage 231 passes from communication with the ,passage 246 over the ungrooved portion 214 of the distributor block 233 until it again comes into open communication with the extended passage .239 which is under direct pump pressure and which serves to hold that chuck closed while in all subsequent operating positions. relatively quick passage over the ungrooved por- During the tion 214 of the distributor block 233. there will be 

